CN104471279A - Centrifugal pendulum - Google Patents
Centrifugal pendulum Download PDFInfo
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- CN104471279A CN104471279A CN201380037520.3A CN201380037520A CN104471279A CN 104471279 A CN104471279 A CN 104471279A CN 201380037520 A CN201380037520 A CN 201380037520A CN 104471279 A CN104471279 A CN 104471279A
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- Prior art keywords
- pendulum mass
- pendulum
- ring
- profile
- synchronizing ring
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/30—Flywheels
- F16F15/31—Flywheels characterised by means for varying the moment of inertia
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
- F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
- F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
- F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
- F16F15/1464—Masses connected to driveline by a kinematic mechanism or gear system
- F16F15/1471—Masses connected to driveline by a kinematic mechanism or gear system with a kinematic mechanism, i.e. linkages, levers
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/21—Elements
- Y10T74/2121—Flywheel, motion smoothing-type
- Y10T74/2128—Damping using swinging masses, e.g., pendulum type, etc.
Abstract
The invention relates to a centrifugal pendulum (10), in particular for arranging on a drive shaft of an internal combustion engine, comprising a driving ring (12) that can be installed on a drive shaft in a rotationally fixed manner and a synchronizing ring (14) that can rotate freely in relation to the driving ring. The axis of rotation of the driving ring (12) and the axis of rotation of the synchronizing ring (14) are identical. The centrifugal pendulum (10) further comprises at least one pendulum body (16) movably supported on the driving ring (12). The pendulum body (16) is kinematically coupled to the synchronizing ring (14) by means of at least one coupling element (18; 40; 42; 44) in such a way that the coupling element (18; 40; 42; 44) deflects the pendulum body (16) toward the axis of rotation when the synchronizing ring (14) rotates in relation to the driving ring (12) in a first direction.
Description
Technical field
The present invention relates to a kind of centrifugal force pendulum, especially for being arranged on the live axle of internal-combustion engine.
Background technique
In four-stroke piston engine, the periodic process of four strokes (air-breathing, compression, acting, exhaust) and the ignition order of each cylinder combine, cause bent axle and rotation nonuniformity that is flywheel that is that be connected to.Drivetrain due to the inertia that within it contains and rigidity but a kind of have unique natural frequency, can the organization system of whirling vibration, so the rotation nonuniformity imported by motor must cause whirling vibration.This whirling vibration must be reduced on tectonic sieving.
The motor that development has a lesser amt cylinder is trend of the times, and reduces rpm level and also in the middle of engine research, development personnel, cause concern.But higher rotation nonuniformity can be caused like this, this rotation nonuniformity needs again new Vibration Absorption Designing scheme.
For reducing the known device of the torsional vibration when torsion load fluctuates and industry explicitly (automotive engineering, naval technology, aeronautical technology, lathe etc.) exist in various different formats.The equipment for reducing torsional vibration be based upon in automotive engineering is such as single mass flywheel or dual mass flywheel and also has centrifugal force pendulum at this, and the combination be made up of each equipment.But known equipment can not meet the requirement (such as smoothness of operation) of the modern industry when the torque load of high and/or low frequency fully.
Need to consider stable running state in the dynamic design of the equipment for reducing the torsional vibration when torque load fluctuates, the particularly operation of machine for doing work (under a load) when rotating speed is almost constant, same needs consider acceleration or the braking of unstable running state, particularly machine for doing work (under a load).Known centrifugal force pendulum equipment has shortcoming in stable running state: stress efficacy is responsive relative to pivot friction, by the pivot angle that dangles limited limit and by constraint geometrical relationship determined.Known centrifugal force pendulum equipment has shortcoming in the running state of instability: maximum pivot angle low friction or in design that damping is weak by the restriction of addition thereto.The quality that can make to dangle is be worth pursuing without the measure of braking with impacting from acoustics viewpoint.The centrifugal force pendulum system set up is insufficient for the realization of this point.
Summary of the invention
The object of the invention is, meet the requirement of the modern industry to the torsional vibration be reduced in when torque load fluctuates better.Particularly should solve the vibration problem during slow-speed of revolution better.
This object is achieved by the centrifugal force pendulum with feature described in claim 1 or claim 2.In the dependent claims to useful being set forth with suitable structure of centrifugal force pendulum according to the present invention.
According to a first aspect of the invention, described centrifugal pendulum especially on the live axle being arranged on internal-combustion engine and comprise a driving ring, a synchronizing ring and at least one be bearing in pendulum mass on driving ring.The feature of this centrifugal force pendulum is: relative to the motion of the pure rotation of supporting point generation synchronizing ring on driving ring and the motion of the pure rotation of pendulum mass.
According to a second aspect of the invention, described centrifugal pendulum is especially on the live axle being arranged on internal-combustion engine and comprise one and torsionally (drehfest, namely the two can not relatively rotate) can install driving ring on the driving shaft and a synchronizing ring that can rotate freely relative to driving ring.The spin axis of driving ring is consistent with the spin axis of synchronizing ring.In addition, centrifugal force pendulum comprises at least one and is bearing in pendulum mass on driving ring movingly.This pendulum mass is kinematically coupled to synchronizing ring by least one coupling element, make coupling element when synchronizing ring rotates along first direction relative to driving ring by the center of gravity of pendulum mass towards rotational axis offset.
Centrifugal force pendulum according to the present invention is based on the principle not identical with known system up to now.The relative torsion of the synchronizing ring that driven driving ring can rotate freely relative to itself causes the center of gravity of pendulum mass to bias internal, but (excessively) that this skew can obtain centrifugal force again compensates.If multiple pendulum mass is coupled to synchronizing ring, need only ensure that the total centre of gravity of the pendulum mass produced can be passed through relative to ensureing to bias internal and again outwards being offset by centrifugal force.This principle can realize the very effective and stable damping of torsional vibration, particularly when the slow-speed of revolution.At this, synchronizing ring provides an additional inert masses, makes total inertia move in this way.If be provided with multiple pendulum mass, synchronizing ring is also used for all pendulum masses synchronously, are in the same manner moved in addition.
The present invention can inter-tradely for compensating the torsional torque of fluctuation.Size relationship (increase/reduce of such as pendulum mass center of gravity relative to the spacing of spin axis and/or the increase/reduction of pendulum mass quality) can be demarcated according to maximum torsional torque peak value.The auxiliary addition thereto of (schwingungsentkoppelnd) of vibration isolation or the system of vibration damping can be used as according to centrifugal force pendulum of the present invention.Particularly can be arranged in the primary side of dual mass flywheel.Generally speaking, this centrifugal force pendulum can be incorporated into vibration isolation well or vibration damping system in.
Vibrate as far as possible equably in order to ensure pendulum mass, coupling element should make synchronizing ring rotate along with first direction (=above-mentioned torsional direction, this torsional direction relative to the skew of pendulum mass toward guided inside) contrary direction relative to driving ring when pendulum mass deviates from rotational axis offset due to centrifugal action.
In principle, pendulum mass can be bearing on driving body movingly by different modes.According to first group preferred embodiment, pendulum mass can be bearing on driving ring rotatably, wherein, and the rotation that coupling element only allows pendulum mass limited.In this case, pendulum mass implements controlled whirling vibration.
Can use rolling element as coupling element, particularly pin, this rolling element can be inserted to unrestricted motion in the profile of space boundary of synchronizing ring and pendulum mass.When driving ring and synchronizing ring are reversed toward each other, profile and (arbitrarily) nonlinear motion that can realize between pendulum mass and synchronizing ring that cooperatively interacts of rolling element can rolled on described profile.Can be realized by the configuration of profile harmonious (tautochroneAbstimmung) of the tautochrone of centrifugal force pendulum.
According to the first preferable configuration of centrifugal force pendulum of the present invention, pendulum mass stretches between two mutual rigidly connected dishes of synchronizing ring, wherein, the profile that coupling element passes pendulum mass from the profile of the first dish extends to a profile of the second dish, and this profile of the second dish is accurately opposed with the profile that first coils.
According to optional second preferable configuration of one, synchronizing ring stretches between two mutual rigidly connected half portion of pendulum mass, wherein, the profile that coupling element passes synchronizing ring from the profile of the first pendulum mass half portion extends to a profile of the second pendulum mass half portion, and this profile of the second pendulum mass half portion is accurately opposed with the profile of the first pendulum mass half portion.
The linear bearings of pendulum mass on driving ring also achieves the useful structure according to centrifugal force pendulum of the present invention, and in described supporting, pendulum mass can move in translation, preferably radially.
Like this, the example as this second group of preferred implementation can arrange line or belt as coupling element, and pendulum mass utilizes this coupling element to be connected with synchronizing ring.So particularly can realize preferred motion in the following way, namely synchronizing ring has the periphery with (can construct as requested) profile, is close on described profile during the relative torsion of line or belt between driving ring and synchronizing ring.
Articulated mechanism also can be used as coupling element, is connected with synchronizing ring by this articulated mechanism pendulum mass.
Another kind of tectonic sieving specifies: pendulum mass is coupled to the outer portion part of synchronizing ring in the following way, and namely pendulum mass is hanging in a roller, and this roller can roll on the profile of synchronizing ring.
Equally, as in rotatable supporting, also can rolling element be used as coupling element in the linear bearings of pendulum mass, particularly pin, this rolling element can be inserted to unrestricted motion in the profile of synchronizing ring and pendulum mass.
Although the basic role principle for centrifugal force pendulum according to the present invention only needs a pendulum mass, multiple with along the circumferential direction distributing pendulum mass be bearing on driving ring also can be utilized to realize higher damping effect when degree of unbalancedness is less.So the total centre of gravity of all pendulum masses must towards rotational axis offset when synchronizing ring rotates along first direction relative to driving ring.
In order to driving ring is coupled to live axle and/or in order to driving ring is coupled to synchronizing ring and/or selectively (difference) elastic element can be provided with to be bearing in by pendulum mass on driving ring.
Accompanying drawing explanation
Other features and advantages of the present invention can be drawn by explanation hereafter and accompanying drawing.Shown in the drawings:
Fig. 1 is the perspective view of the first mode of execution according to centrifugal force pendulum of the present invention;
Fig. 2 is the centrifugal force pendulum in Fig. 1, does not have the lid of synchronizing ring, and has the second dish reduced;
Fig. 3 is the perspective view of a multi-part type synchronizing ring;
Fig. 4 is the perspective view of pendulum mass;
Fig. 5 is the perspective view of the second mode of execution according to centrifugal force pendulum of the present invention, and this centrifugal pendulum has the pendulum mass illustrated pellucidly;
Fig. 6 is the schematic plan of the 3rd mode of execution according to centrifugal force pendulum of the present invention;
Fig. 7 is the schematic plan of the local of the 4th mode of execution according to centrifugal force pendulum of the present invention;
Fig. 8 is the schematic plan of the local of the 5th mode of execution according to centrifugal force pendulum of the present invention; With
Fig. 9 is the schematic plan of the local of the 6th mode of execution according to centrifugal force pendulum of the present invention.
Embodiment
Centrifugal force pendulum 10 according to the first mode of execution has been shown in Fig. 1 or Fig. 2, this centrifugal force pendulum can as have internal-combustion engine Motor Vehicle drivetrain in torshional vibration damper.The coupling element of the chief component of centrifugal force pendulum 10 to be a driving ring 12, synchronizing ring 14, multiple pendulum mass 16 and multiple form be herein pin 18.
Driving ring 12 is torsionally coupled with the live axle of any one in drivetrain, and can be such as the primary side of dual mass flywheel or be torsionally coupled to this primary side.In order to realize driving ring 12 and live axle or with being coupled of the primary side of dual mass flywheel, selectively can arrange one and be connected to middle elastic element (elasticity is coupled).
Synchronizing ring 14 utilizes sliding bearing or rolling bearing to can be rotated to support on driving ring 12 or on live axle.Importantly: synchronizing ring 14 itself freely can rotate relative to driving ring 12.The spin axis of driving ring 12 is coaxial with the spin axis of synchronizing ring 14, that is is consistent.
In addition, multiple pendulum mass 16 utilizes sliding bearing or rolling bearing 20 to can be rotated to support on driving ring 12.The bearing 20 of pendulum mass 16 is about rotation axis off-center and be so arranged on driving ring 12, that is, pendulum mass 16 can turn at the plane internal rotation perpendicular to running shaft.A unique pendulum mass 16 is also just enough in principle; But hereafter with multiple equally distributed pendulum mass 16 for starting point, as shown in the embodiment of Fig. 1 and 2.
Show separately in figure 3 relative to the rotatable synchronizing ring 14 of driving ring 12.Synchronizing ring 14 is configured to multi-part type herein.On that side of driving ring 12, be provided with the first dish 22 at pendulum mass 16, and be provided with the second dish 24 on that side of the driving ring dorsad 12 of pendulum mass 16.Two dishes 22,24 connect mutually rigidly.
Also can arrange a thick dish replaces two to coil 22,24, and wherein, the intermediate spaces between two dishes 22,24 are replaced by one or more groove, and pendulum mass 16 stretches in described groove.
That side of the driving ring dorsad 12 of the second dish 24 is provided with lid 26, and this lid is fixed on the second dish 24.Lid 26 also can construct with second with coiling 24 single types.Tightening pin 28 is for making two dishes 22,24 mutual accurately, directed definitely in advance.
Two dish 22,24 in be processed with multiple preferably identical profile 30 respectively with along the circumferential direction distributing, wherein, first dish 22 profile 30 and second coil 24 profile 30 just in time accurately opposed.Can't see the profile of the second dish 24 in fig. 2, because only show the part of the inside from the second dish 24, to see the pendulum mass 16 hereafter more described in detail.
Preferably identical pendulum mass 16 preferably respectively to become uniform distances ground with spin axis, to be bearing on driving ring 12 swingably, illustrates separately in described pendulum mass in the diagram.Each pendulum mass 16 has a profile 32.The center of gravity of the pendulum mass 16 that utilized 34 to mark, the position of this center of gravity by pendulum mass 16 general shape and determined by the structure of the vacancy mouth 36 in pendulum mass 16 alternatively.
The pendulum mass 16 be bearing on driving ring 12 is coupled to synchronizing ring 14 by pin 18.Pin 18 is inserted in profile 30 or 32, and the profile 32 that each pin 18 passes pendulum mass 16 from the profile 30 of the first dish 22 or rather extends to the opposed profile 30 of the second dish 24.Pin 18 is not neither also connected with pendulum mass 16 with synchronizing ring 14.
Pin 18 1 aspect extends axially through driving ring 12 and fixes, and this driving ring prevents pin 18 from deviating from from the profile 30 of the first dish 22.For making pin 18 can not deviate from from the profile 30 of the second dish 24, be provided with lid 26.But optionally, also other cover plates can be set, or, dish 22,24 in profile 30 can be only vertically have certain degree of depth and and non-penetrating.In order to axial restraint also can make pin 18 be configured with flange.
Pin 18 and synchronizing ring 14 and the profile 30,32 of pendulum mass 16 so mutually coordinate, that is, while synchronizing ring 14 is reversed relative to driving ring 12, pendulum mass 16 can carry out limited rotary motion around its bearing 20.At this, pin 18 is used as the rolling element rolled on profile 30,32.
Profile 30,32 and pin 18 usually can realize (arbitrarily) nonlinear motion between pendulum mass 16 and synchronizing ring 14.The harmonious of the tautochrone of centrifugal force pendulum 10 can be realized by the configuration of the profile 30,32 matched with pin 18.
Hereafter the basic role principle of centrifugal force pendulum 10 is set forth.
Fig. 1 and 2 illustrates a state of centrifugal force pendulum 10, does not have torsion to work in a state in which or pendulum mass 16 offsets to greatest extent.If engine start and live axle rotate, this live axle drives described driving ring 12.Rotatable synchronizing ring 14 is due to the first and then rotation of its inertia.Between driving ring 12 and synchronizing ring 14, consequent torsion causes pin 18 so to roll on profile 30,32, namely, pendulum mass 16 is to bias internal, and or rather, the total centre of gravity of the pendulum mass 16 drawn by the position of all centers of gravity 34 of each pendulum mass 16 is vacillated to the direction of spin axis.
But further rotating in process, pendulum mass 16 is pulled outwardly by centrifugal force.Therefore, pendulum mass 16 so degree ground outwards skew, that is, the pin 18 rolled in profile 30,32 forces synchronizing ring 14 to be reversed relative to driving ring 12, but along contrary sense of rotation.This point finally causes synchronizing ring 14 to exceed driving ring 12 in short time after certain rotation.But, between driving ring 12 with synchronizing ring 14 along the relative torsion of contrary sense of rotation again cause pendulum mass 16 by via pin 18 kinematically be coupled and to bias internal.
Repeat these processes, just make pendulum mass 16 produce and swing.Kinematic relation between the relative torsion and the skew of pendulum mass 16 of synchronizing ring 14 and driving ring 12 is by the quality of pendulum mass 16 and the inertia of synchronizing ring 14 and determined by the type of vibrational excitation.At this, synchronizing ring 14 provides additional inert masses, and thus, total inertia just moves.In addition, synchronizing ring 14 is used for all pendulum masses 16 synchronously, are similarly moved.
When live axle rotates equably, that is, when applying constant moment of torsion on the driving shaft through the long period, centrifugal force pendulum 10 gradually stops swinging and occurs a kind of state of equilibrium.But as general in internal-combustion engine, if there is torque ripple owing to rotating nonuniformity, excitation centrifugal force pendulum 10 vibrates.So the torsional vibration be used in damping drivetrain effectively of oscillating mass.
In order to limit the relative torsion between driving ring 12 and synchronizing ring 14, flexible coupling element can be set between these two rings.For this reason, such as the supporting point place of synchronizing ring 14 directly just on live axle or driving ring 12 is connected with the element of an elastically deformable.
Equally, bearing 20 also can have flexible coupling element, and described coupling element affects the oscillating motion of pendulum mass 16 relative to driving ring 12 targetedly.For this reason, such as the supporting point place of pendulum mass 16 directly on driving ring 12 is connected with the element of an elastically deformable, and described element is fixedly connected with driving ring 12 in that at it.
In addition, an additional device can be set, utilize this device synchronizing ring 14 can be made on one's own initiative along sense of rotation braking or accelerate.
Figure 5 illustrates the second mode of execution of centrifugal force pendulum 10.The different tectonic sieving of synchronizing ring 14 and pendulum mass 16 are from the main difference part of aforementioned embodiments.
Half portion 16a, 16b that pendulum mass 16 has gap therebetween by two substantially at this are formed.Upper pendulum mass half portion 16a, 16b are rigidly connected mutually in place, thus they can rotate around bearing 20 jointly.Optionally, pendulum mass 16 also can be equivalent to gap groove single type construct.Each pendulum mass half portion 16a has a profile 32, and this profile is just in time opposed exactly with the consistent profile 32 of another pendulum mass half portion 16b.
In contrast, synchronizing ring 14 is then integrally configured to independent dish at this.The profile 30 of synchronizing ring 14 is through.Synchronizing ring 14 is rotatably arranged between pendulum mass half portion 16a, 16b.
Again by insert in profile 30,32, freely pin 18 realize pendulum mass 16 and synchronizing ring 14 being coupled kinematically.At this, the profile 30 that pin 18 passes synchronizing ring 14 from the profile 32 of a pendulum mass half portion 16a extends to the profile 32 of opposed pendulum mass half portion 16b.
Pin 18 is fixed by driving ring 12 vertically in side; On another side or cover plate can be arranged on pendulum mass half portion 16b.Or profile 32 is only have certain degree of depth and non-penetrating vertically in pendulum mass half portion 16a and/or 16b.
The action principle of centrifugal force pendulum 10 conforms to the first mode of execution, and that is, the effect of synchronizing ring 14 is to make pendulum mass 16 with the form of torsional vibration around bearing 20 synchronous hunting.
In Fig. 6 to 9, schematically show four other mode of executions of centrifugal force pendulum 10, pendulum mass 16 is not rotatably but can is bearing in the corresponding guide portion 38 of driving ring 12 with moving radially in these embodiments.At this, hereinafter same with multiple pendulum mass 16 for starting point, although an independent pendulum mass 16 also only can be arranged.
In mode of execution shown in Figure 6, pendulum mass 16 is connected with synchronizing ring 14 by line or band 40.Synchronizing ring 14 itself has the periphery with the contoured 30 for line or belt 40, and described line or belt is used for replacing pin 18 that pendulum mass 16 is kinematically coupled to synchronizing ring 14 at this.By the tectonic sieving of profile 30, be kinematicly coupled the requirement that can be matched with and determine.
Be similar in the foregoing embodiment, synchronizing ring 14 causes pendulum mass 16 towards spin axis displacement in guide portion 38 relative to the torsion of driving ring 12, because line or belt 40 to be clung on profile 30 and inwardly drawn by the total centre of gravity of pendulum mass 16 or pendulum mass 16 by their skews along sense of rotation.Owing to being designed to linear guide portion 38, the displacement of pendulum mass 16 in this case translation.Centrifugal force is again for being pulled outwardly pendulum mass 16, thus synchronizing ring 14 is reversed relative to the sense of rotation of driving ring 12.Repeat the vibration that these processes cause centrifugal force pendulum 10.
In the figure 7 the mode of execution of shown centrifugal force pendulum 10 and the mode of execution of Fig. 6 closely similar.At this, replace line or belt 40, have an articulated mechanism 42 to be used for realizing kinematic being coupled respectively.Contoured in synchronizing ring 14 is not specified, because be responsible for fatefully ensureing vibration characteristics in the design at first determined in detail of this articulated mechanism 42.
In the embodiment shown in figure, pendulum mass 16 equally also can be bearing in the corresponding guide portion 38 of driving ring 12 with moving radially.Pendulum mass 16 is coupled to the outer portion part of synchronizing ring 14 in the following way at this, that is, described pendulum mass 16 utilizes a line or belt 40 to be hanging in a roller 44 respectively, and described roller can roll on the inner side profile 30 of the outer portion part of synchronizing ring 14.
The difference of mode of execution shown in Fig. 9 and aforementioned embodiments is: replace roller 44 to be provided with pin 18 and replace line or belt 40 to be provided with profile 32 in pendulum mass 16.Pendulum mass 16 has the shape of " U " at this and is surrounded by the outer portion part of synchronizing ring 14 with its two edges of a wing.Two edges of a wing have profile 32 accurately opposed each other respectively.Pin extends to opposed profile 32 from a profile 32 and meanwhile passes the profile 30 of synchronizing ring 14.Profile 30,32 is so mutually harmonious, namely, during relative torsion between driving ring 12 and synchronizing ring 14, pendulum mass 16 or their total centre of gravity are inwardly pressed, and synchronizing ring 14 is reversed relative to the sense of rotation of driving ring 12 when pendulum mass 16 outwards moves due to centrifugal action.
The mode of execution be described all has following common ground: pendulum mass 16 is kinematically coupled to synchronizing ring 14, thus ensures identical, the synchronous skew of all pendulum masses 16 all the time.The mode of execution in principle with an only pendulum mass 16 is also possible, as long as this pendulum mass is kinematically coupled to synchronizing ring 14.
Also described to be kinematicly coupled can be realized by the combination of different designs scheme.The translational guidance of the possible scheme for linear guide well known in the prior art (such as swallow-tail form guide portion, wedge shape guide portion etc.) enforcement to pendulum mass 16 can be utilized.Preferred pendulum mass 16 one-tenth cylindrical structure and in a cylindrical body matched therewith guide (being similar to the piston in internal-combustion engine).In addition, in order to be bearing on driving ring 12, pendulum mass 16 can be coupled to the element of an elastically deformable, and this element is then coupled to driving ring 12 again at it in that regularly.
As can learning from accompanying drawing, should not be construed restrictive for the title selected by each parts of centrifugal force pendulum 10.Particularly, driving ring 12 and synchronizing ring 14 need not have the traditional form of ring body, but can have shape design unlike this respectively.
Reference numerals list
10 centrifugal force pendulums
12 driving rings
14 synchronizing ring
16 pendulum masses
16a first pendulum mass half portion
16b second pendulum mass half portion
18 pins
20 bearings
22 first dishes
24 second dishes
26 lids
28 tightening pins
30 profiles (synchronizing ring)
32 profiles (pendulum mass)
34 centers of gravity
36 vacancy mouths
38 guide portion
40 line or belts
42 articulated mechanisms
44 rollers
Claims (14)
1. centrifugal force pendulum (10), especially for being arranged on the live axle of internal-combustion engine, it comprises: driving ring (12); Synchronizing ring (14); Be bearing in the pendulum mass (16) on described driving ring (12) with at least one, it is characterized in that: relative to the supporting point on described driving ring (12), the motion of described synchronizing ring (14) pure rotation and the motion of described pendulum mass (16) pure rotation occur.
2. centrifugal force pendulum (10), especially for being arranged on the live axle of internal-combustion engine, it comprises:
Driving ring (12) on the driving shaft can be torsionally installed,
The synchronizing ring (14) that relative driving ring (12) can rotate freely, wherein, the spin axis of described driving ring (12) is consistent with the spin axis of described synchronizing ring (14), and
At least one is bearing in the pendulum mass (16) on described driving ring (12) movingly,
Wherein, described pendulum mass (16) is kinematically coupled to described synchronizing ring (14) by least one coupling element, makes described coupling element (18; 40; 42; 44) when described synchronizing ring (14) rotates along first direction relative to described driving ring (12) by the center of gravity of described pendulum mass (16) towards rotational axis offset.
3. centrifugal force pendulum (10) as claimed in claim 2, is characterized in that: when the center of gravity of described pendulum mass (16) deviates from rotational axis offset due to centrifugal action, described coupling element (18; 40; 42; 44) described synchronizing ring (14) is made to rotate along direction opposite to the first direction relative to described driving ring (12).
4. centrifugal force pendulum (10) as claimed in claim 2 or claim 3, it is characterized in that: described pendulum mass (16) can be bearing on described driving ring (12) rotatably, wherein, described coupling element (18) only allows described pendulum mass (16) limitedly to rotate.
5. the centrifugal force pendulum (10) as described in any one of claim 2 to 4, it is characterized in that: described coupling element (18) is rolling element, particularly pin, this rolling element can insert to unrestricted motion described synchronizing ring (14) with in the profile (30,32) of the space boundary of described pendulum mass (16).
6. centrifugal force pendulum (10) as claimed in claim 5, it is characterized in that: described pendulum mass (16) stretches into two mutual rigidly connected dishes (22 of described synchronizing ring (14), 24) between, wherein, described coupling element (18) extends to a profile (30) of the second dish (24) from the profile (30) of the first dish (22) through the profile (32) of described pendulum mass (16), and this profile of described second dish coils (22) described profile (30) with described first is accurately opposed.
7. the centrifugal force pendulum (10) as described in any one of Claims 1-4, it is characterized in that: described synchronizing ring (14) stretches into two mutual rigidly connected half portion (16a of described pendulum mass (16), 16b), wherein, described coupling element (18) extends to a profile (32) of the second pendulum mass half portion (16b) from the profile (32) of the first pendulum mass half portion (16a) through the profile (30) of described synchronizing ring (14), this profile of described second pendulum mass half portion is accurately opposed with the described profile (32) of described first pendulum mass half portion (16a).
8. centrifugal force pendulum (10) as claimed in claim 2 or claim 3, is characterized in that: described pendulum mass (16) preferably radially can be bearing on described driving ring (12) movably in translation.
9. centrifugal force pendulum (10) as claimed in claim 8, it is characterized in that: described coupling element is line or belt (40), described pendulum mass (16) utilizes this coupling element to be connected with described synchronizing ring (14), and, described synchronizing ring (14) has the periphery with profile (30), and described line or belt (40) clings on described profile when having during relative torsion between driving ring (12) and synchronizing ring (14).
10. centrifugal force pendulum (10) as claimed in claim 8, it is characterized in that: described coupling element has articulated mechanism (42), described pendulum mass (16) is connected with described synchronizing ring (14) by this articulated mechanism.
11. centrifugal force pendulums (10) as claimed in claim 8, it is characterized in that: described pendulum mass (16) is coupled to the outer portion part of described synchronizing ring (14) by following manner, namely, described pendulum mass (16) is hanging in roller (44), and this roller can in the upper rolling of the profile of described synchronizing ring (14) (30).
12. centrifugal force pendulums (10) as claimed in claim 8, it is characterized in that: coupling element is rolling element, particularly pin (18), this rolling element can insert to unrestricted motion described synchronizing ring (14) with in the profile (30,32) of described pendulum mass (16).
13. centrifugal force pendulums (10) as described in any one of aforementioned claim, it is characterized in that: on described driving ring (12), be along the circumferential direction supported with multiple pendulum mass (16) to distribution, wherein, when described synchronizing ring (14) rotates along first direction relative to described driving ring (12) total centre of gravity of all pendulum masses (16) towards rotational axis offset.
14. centrifugal force pendulums (10) as described in any one of aforementioned claim, is characterized in that: in order to described driving ring (12) is coupled to live axle and/or in order to described driving ring (12) being coupled to described synchronizing ring (14) and/or upper and be provided with elastic element in order to described pendulum mass (16) being bearing in described driving ring (12).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102012016924 | 2012-08-27 | ||
| DE102012016924.8 | 2012-08-27 | ||
| PCT/EP2013/067455 WO2014033043A1 (en) | 2012-08-27 | 2013-08-22 | Centrifugal pendulum |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104471279A true CN104471279A (en) | 2015-03-25 |
| CN104471279B CN104471279B (en) | 2016-11-16 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380037520.3A Active CN104471279B (en) | 2012-08-27 | 2013-08-22 | centrifugal force pendulum |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US9915317B2 (en) |
| EP (1) | EP2888506B1 (en) |
| CN (1) | CN104471279B (en) |
| WO (1) | WO2014033043A1 (en) |
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Also Published As
| Publication number | Publication date |
|---|---|
| US20150167779A1 (en) | 2015-06-18 |
| EP2888506A1 (en) | 2015-07-01 |
| EP2888506B1 (en) | 2020-02-26 |
| US9915317B2 (en) | 2018-03-13 |
| WO2014033043A1 (en) | 2014-03-06 |
| CN104471279B (en) | 2016-11-16 |
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